Multiple unit compact gear divider assembly



' Oct. 9', 1945;

J. A. LAUCK MULTIPLE UNIT 'COMPACT GEAR DIVIDER ASSEMBLY Filed April 15, 1945 6 Sheets-Sheet 1 Oct. 9, 1945. J. A. LAUCK 2,386,219

A MULTIPIE UNIT COMPACT GEAR DIVIDER ASSEMBLY Filed April 15, 1943 6 Sheets-Sheet 2 Oct. 9, 1945. J. A. LAUCK MULTII LE UNIT COMPACT GEAR DIVIDER ASSEMBLY Filed April 15, 1943 6 Sheets-Sheet 4 I Oct. 9, 1945. J. A. LAUCK MULTIPLE UNIT COMPACT GEAR DIVIDER ASSEMBLY e Sheets-Sheet 5 Filed April '15. 1943 Oct. 9, 1945. LAUCK MULTIPLE UNIT, COMPACT GEAR IJIVIDER ASSEMBLY Filed April 15, 1943 6 Sheets-Sheet 6 Patented Oct. 9, 1945 COMPACT GEAR DIVIDER,

SEMBLY MULTIPLE UNIT John A. touch, South Euclid, Ohio, asslgnor to [I Pesco Products 60., Cleveland, Ohio, a corporatlon of Ohio Application April 15, 1943, Serial No. 483,119

9 Claims. (01.103-11') This invention is a continuation-in-part of the application of John A. Lauck, Serial No. 314,209, now Patent No. 2,343,912, March 14, 1944, and

relates to a fluid system and the like. More par-- ticularly, this invention relates to improved means for equalizing the flow of fluid to a plurality of remotely located hydraulically operated units.

, It is a principal object of this invention to disclose an improved means for synchronizing the movement of a plurality of remotely located fluid pressure operated instrumentalities. In this con-' nection, it is an object to provide an improved means for dividing and metering a flow of fluid between a plurality of instrumentalities to be operated, so that they may be operated in a constantly maintained relationship regardless of possible varying operating conditions, and irrespective of whether one of the said instrumentalities has a greater pressure or drag thereon than the other or others.

' It has been found thatfixed displacement iluid pumps, especially or the so-called gear type, vary their output flow somewhat in relation to the resistance to flow exerted on the output of said pump. This variation in output flow is of serious consequence in the case where a plurality of instrumentalities are to be operated in synchronism,

such, for example, as is the casein operating the wing flaps or landing gears of an airplane. A difierence inflow to a fluid motor of one wing flap as compared to the other may throw an airplane I out of balance, with serious consequences. It is necessary,

therefore, to provide means compensating for and adjusting any difierence in the ratio of flow, whereby such instrumentalities will be automatically maintained incorrect synchronism, and it is an object 01' this invention to disclose an improved means accomplishing this purpose.

' In connection with the above, it is an obiectto provide, in connection with a fluid moving flow divider which has a plurality of outlets and which flow divider may be actuated by the pressure of the inlet stream or may be driven by power means such as an electric motor, or both. It 'is particularly an object to disclose an improved device operable from a source of power such as an electric motor.

It is a further object of the invention to provide a system for accomplishing the above-mentioned purposes, in which there is provided an improved throttling valve arrangement in connection with a fluid dividing and moving means, and wherein the throttling valve arrangement assures correct amount of fluid flow to eachof the instrumentalitles to be operated.

It is another object to provide anarrangement in which a flu'id moving flow divider has a single .inlet and a plurality of discharge outlets or conduits, each of which discharge conduits in turn has a second fluid moving flow divider,with a plurality of dischargec'onduits thereon, and as an alternative construction an improved means for boosting. the flow from each divider.

It is a further and important object of this invention to combine what may be termed the fluid moving gear divider unit and the back pressure equalizer valve assembly in a single housing in a novel and compact manner.

It is a purpose to disclose an improved back pressure equalizingvalve assembly incorporating ball type check valves, which arrangement is advantageousover other means which are employed in similar situations, and in addition which ball type valve eliminates the need for the use of at least one flexible seal for each valve, said seal being usually composed of rubber or a synthetic product, or other very scarce materials.

It is a further object to provide a novel assembly v in which the fluid" stream is divided once, and

varies the amount of fluid. moved from any one outlet in relation to the resistance to flow 01' any such outlet, means responsive to such resistance in flow in one outlet, which varies the resistance in the other outlet or outlets whereby the resist ance in all outlets are substantially proportional or identical at all times.

It is another object to provide an assembly for accomplishing the synchronized operation oi a plurality of remotely located, independently operable devices; in this connection it is an object to provide a device which is relatlv ly simple to manufacture, is comparatively'co pact and inexpensive, and p rated,

It is a further object of this invention to provide a fluid movingflow divider for operating a one which iseaslly serviced" and plurality of synchronized'instrumentalities, which invention will-become after consideration of the '01 the specification, 'Whereln:

each of the resultant streams is in turn divided into four streams by a novel combination of compact flow dividers, occupyingcomparatively little space'and suitable for installation on such devices as aircraft.

It is a still further object to disclose a gear type fluid moving flow divider in which there are less sets of. gears than there are outlet streams, for 1 example, in which. three sets of gears comprising "two groups of three gears each, have four outlet streams. I Other objects, the

ing the following specification and claims, and drawings forming a part F'ig. 1 is a schematic diagram, showing the device of the'present invention as applied to an airplane of conventional design, for the purpose of operating the wing flaps thereof;

Fig. 2 is an elevational cross-sectional view taken on the line 2-2 01 Figs. 1 and 3, looking advantages and uses 0! the more apparent after read-' taken on the line -4 able to many other -uses.

cover the openings respectively, of return con-.

in the direction of the arrows, and showing a de-,

vice which may be termed a gear type two-way fluid moving flow divider;

Fig. 3 is a horizontal cross-sectional view taken on the line 3-! 01 Fig. 2, looking inthe direction of the arrows;

Fig. 4 is a vertical elevational view, partially in cross-section, taken on the line 4-4 of Fig. 2,

looking in the direction of the arrows;

Fig. 5 is a fragmentary cross-sectional view direction of the arrows;

, Fig. 6 is a view of what may be termed a gear type four-way fluid moving flow divider, showing schematically the arrangement of fluid circuits in said divider;

Fig. 7 is a longitudinal, elevational sectional view oi the tour-way fluid moving flow divider shown as part of schematic Fi 6. theview being taken on the line 1-1 of Fig. 9, looking in the, direction of the arrows;

Fig 8 is a cross-sectional, elevational view taken on the line 8-8 of Fig. 7, looking in'the direction of the arrows;

Fig.9 is a cross-sectional, elevational view,

. taken on the line 9-9 of Fig. I, looking in the direction of the arrows;

of Fig. 4, looking in the Fig. 10 isa cross-sectional elevational view taken'on the line lU-lfl of Fig. 'I, looking in the direction of the arrows;

Fig. 11 is a fragmentary, horizontal, cross-sectional view, taken on the line llll of Fig. 8,

looking in the direction of the arrows; and

Fig. 12 is a fragmentary, partial sectional view showing a fluid moving flow divider driven bya power means such as an electric motor.

Referring, more in detail to the construction shown in the various figures, and referring first to Fig. 1, the present invention has been indicated as applied to an aircraft of conventional design for the purpose of operating the wingflaps thereon. It will be understood that while primarilyillustrative, and the invention is adapt- The airplane 20 shown in dotted vided with the wing flaps 22 and 24. These wing flaps 22 and-24 are operated by means of what may be termed ahydraulic system indicated generally by the numeral 26; Thi system is schematically illustrated in Fig. l.

' It comprises'in the combination and arrangement herein shown, a control means herein referred to as control 28, located within the cabin of an airplane, or otherwise, as may be convenient, with an inlet conduit "leading from an 4 blocked or brought 3 this application of the invention is a particularly advantageous one, it may be considered lines, is proaccumulator or a pump (not shown), and an out-l let 32 to a storage tank or the like (not shown). The control means. is likewise provided with two other conduit means, the conduit 35 which lies between the control means and theinlet of a two-way flow divider 34, and a second conduit 36, hereinafter termed reverse conduit, described more in detail later herein.

The control 28 is shown as provided with valve element 38, which segregates the interior of the control means into what may be termed sections 40, 42 and ,sections 40 and 44 vary-'- ing in size with the movementoi, the valve 38, and section 42 varying in position with the movement conduit 36 to flow into respectively.

duit 36 and conduit 35. The conduits 3t and 35 ordinarily enter the control valve means at spaced intervals. The partitions 46 and 48 are spaced apart a distance equal to the spacing of the conduits 35 and 36. This permits the partitions 48 and 48 to be moved into a position which off the openings of said the device in position entirely blocks and closes conduits, thereby locking so that the fluid is static and all of the parts 1 in the system are retained against'movement which would change the position 01 the wing flaps.

The inlet conduit ill is preferably positioned to open into the section 42, regardless of the position of the partitions 48 and 48. The partltions 46 and 48 may be actuated by any convenient means, such as by a lever or by a solenoid arrangement. I

There is provided a by-pass 50, connecting the end sections 40 and 44 together, said by-pass en-' tering each section between the respective conduit 35 or 36, and the end of the housing. This bypass 50 allows fluid entering the section 44 from the section 40 from where it is withdrawn by means of the outlet conduit 32, and may be returned lator.

The conduit :5 is shown in Fig. 1 as leadingz It is understood that the arrangement shown here involving a two-way divider 34, and a pair of tour-way dividers, 58 and 58, is very advantageous 'tor the operation of the wing flaps of an airplane such as is illustrated in the Fig. 1. However, ior other purposes, or for other arrangements of the same purpose, the number of outlets in the dividers 'may be different-and the showing here illustrates the principle involved. I

I The flow divider- 56 is shown as provided with four outlets 60, 52, B4 and 84, leading to theflap operating piston type fluid motors 88, 10, I2 and 14 respectively. Likewise, the tour-way fluid moving flowv divider It is shown as having the four outlets I, 83, 85 and 81, leading to the piston type fluid motors 89, H, 13 and 15 respectively. These correspond to the outlets and fluid motors in connection with the tour-way fluid moving flow divider".

- The'details or construction of the fluid motor 18' used here for illustration are shownin dotted lines, but any form at suitable device may be used.

of the valve 38,-section 42 being-located between sections 40 and.

The valve 38 is provided with cross members 46 and 48 of suflicient width in cross-section to In the arrangement shown, all or the fluid-motors I8, 40, 14, ll, 12, l3, l4 and I5 have leadsq ll connecting to the reverse conduit". While it is not necessaryin the disclosure hereof, dividers,

and equalizers may be inserted in the return conduit.

In normal operation all of these conduits abovedescribed as well as the dividers, control means,

etc., are normally filled with fluid under pressureQ Control of the fluid motors and hence the wing flaps, is obtained by moving the fluid back and forth in the system-so that the position of the pistons 18 in the fluid motors wlll'be varied unto the tank or accumu- 82, and the covers or sides ,84 and 86. The center plate 82 is provided with the overlapping gear wheel receiving bores or recesses 88 and 90, into which are placed the gears comprising the gear wheels 92, 94, 96 and 98, the first two gear wheels meshing and the second two gear wheels meshing in the well known manner of gear pumps. Each pair of gear wheels on the same shaft is usually referred to herein a a set of gear wheels.

The gear wheels (see Figs. 2 and 4) 92 and 96 are preferably providedwith the same axle I to which they may be splined or otherwise attached so as to be driven together. is shown as provided with the splines I02 which accomplishes the purpose of holding the gear .wheels 92 and 96 in synchronism. These splines The axle I00 charge port I28. -The discharge port I26 connects to the pipe 54 above described, and the discharge port I28 connects to the pipe 52 above described. The valve chambers I22 and I24 are connected together by means of a channel I30, preferably at-a position approximately at I32 where an annulus is formed in each valve chamber.

The valve chambers I22-and I24 as above mention'ed each contain what may be termed throttling valves or equalizing valves, valve chamber I22 having the throttling valve I34, and the valve chamber I24 containing the throttling valve I36. It is very desirable that these valves be located in the same housing as the gear pump. They are interconnected hydraulically through the passage I30 as above described, so that a compact and efilcient fluid moving flow dividing and metering means results. Since the construction of these bushings I04, and may be journaled to rotate on The gear wheel 94 will mesh with the gear wheel 92 and the gear wheel 98 will mesh with the that is necessary here.

Accordingly, referring to the throttling valve I36, as particularly illustrated in Fig. 3, there is provided the cup. I38 which is seated against a shoulder formed in the wall of the valve chamber I24, adjacent the outlet port I20. This cup I38 .has an opening in what may be termed its botthe cup I38 forms a valve seat against which the head of the valve I40 is urged by the spring .I42. The valve I40 comprises a cylindrically shaped tubular member and has the upper or head end ports I46.

the sub-chamber and bore of the valve I40, as

gear wheel 98, and it is thus assured that they will be rotated in synchronism.

Referringnext primarily to Figs. 3 and 4, although occasional reference is made to Figs. 2v and 5, the inlet chamber I I0 i shown as located in the center plate 82, which inlet chamber is provided with openings or ports I I2 and I I4, one

of which (H4) leads to the recess 88 on the inlet divided into two streams as it flows from the condult 35 into the two ports I I2 and I I4.

The recesses 88 and 90 are each providedwith an outlet port, the port II8 entering the recess 88, and the port I20 entering recess 90, 'which ports conduct the fluid from the respective gear wheel groups or in reversing operation, to the gear wheels. ,The port II8 leads to the valve chamber I22, and the port I 20 leads to the valve chamber I24.

Located in each of these valve chambers I22 and I24 are means comprising what may be termed a throttling or equalizing valve, by which the amount of fluid pumped by each group of gear wheels is regulated and metered with respect to the amount pumped by any other group in the device. The valve chamber I22 has a discharge port I26, and the valve chamber I24 has a dishereinafter more, fully described. The valve chambers I22 and I24 are'closed by means of the plugs I50, which may havetubular skirt or side wall portions extending upwardly into the chamber I24 (as shown in Fig, 3) preferably to a position just below theport I28. Preferably the plug I50 has a portion I52 of enlarged diameter, which forms a fairly close fit with the wall of the valve chamber. The upper end of the skirt of the plug I50 preferably forms .the seat for a ring type seal I54,

which bears against the washer I56. The washer I56 in turn seats against a shoulder formed inside lection and conduction of fluid, This annulus,

as will most clearl be apparent from Fig. 5, ,v opens into the conduit I30 leading to the other. valve chamber. threaded into the valve chambers and if desired,

The plugs I50are preferably a seal such as a gasket may be provided between the head of the plug I50 and the end of the housing forming the chamber.

The plug I50 likewise has a port means I58 which passes through the skirt of the plug and.

discharges into the annulus I32. The interior bore of. the skirt of theplug I50 preferably forms a cylinder which receives the assembly comprising the valve I40 and the disc valve I48 carried thereby. This assembly above men- 'tioned is so fltted into the skirt of the plug I50 purpose the throttling introduced.

that it is movable axially for seating and unseating-the head of the valve I40 against the shoulders of the cup- I38. If desired, a small clearance may be provided .between the valve. I40 and the wall of the cylindrical bore-of the plug I50, in order that fluid under pressure may be forced between the two in rather minute quantities. This provides for the passage of some fluid from the port I28 downwardly between the walls of the plug I50 and the valve I40 'at the area indicated at I60, for example, and the discharge of that fluid into-the chamber I62 formed in the head end of the plug I50. A one-way" seal I64, preferably ot neoprene or other flexiblematerial, allows this fluid to flow-into the chamber I82, but

prevents its return through the minute space between the walls at I60.

As above mentioned, and as is clearly apparent from Fig. 3, the valve I48 preferably has a depending stem portion which extends through the bore in the body portion of the valve I40 and tie-- pends into the chamber I62 when in assembled position; A cup-like spring seat I86 may be placed over the end of the stem of the valve I48, and between the spring I68 and the bottom of the g body portion of the valve I40. The spring I68 in turn: is carried on a ferrule-like member I10,

which is attached to the end: of the stem of thevalve I48 .by any convenient means such as a pin III. Through this arrangement, the spring I68 exerts tension betweenthe valve I48 and the valve I40, holding the valve I48 seated on the valve seat formed for that purpose on the head'of the valve I40. However, where there is a reversal of the flow of fluid, the valve I48 is unseated by the force of the fluid,'-in which case the valve I48 will move upwardly against the pressure of the spring I68. The valve assemblies I34 and I38 are of substantially the same construction, the valve I34 communicating with the discharge port I28, and the valve I36 communicating with the. discharge port I28. v

It is noted that the stem'of the valve I88 has a slight clearance with respect to the bore of the valve- I40 through'which the said stem passes,

.0001 of an inch, through which fluid under pressure may pass.v

It is understood that in normal operations, the various passages and chambers will be substantially filled with fluid at all times, but the'pressures in such fluid willvary in accordan'cewith the drag or load on the wing flaps. It is further understood that the gears 92 andv86 may be connected to a shaft to which a source of power is" attached, although such connection with a source of pow'erls not shown in Figs. 2, 3, 4 and 5.

Ordinarily, fluid under pressure from the controlmeans 28, is introduced through the inlet atthe outlet port I20 and at the outlet port H8.

This variation is normally suflicient to throw the plane out of balance, and such variation must be compensated for or counteracted, for which valves I38 and I34 are This fluid from the outlet port I20 will pass through the 'cup I38 into the chamber I24, where it will exert pressure on the top of the valves I40 and I48, unseating the valve I40 and causing a downward movement of said valve. (with its assembled parts as previously disclosed), the

fluid flowing from the cup I38 past the valve head of the valve I40 into the discharge port I28, from where it goes to the device. to be operated thereby, in this instance a four-way fluid moving flow divider 56.

Intake event the pressure at the outlet port I28 is Increased, as by drag on the wing flaps, there is a tendency of the head of the valve I40 to seat (in the illustrated position in Fig. 3), or at least to seat partially, so that there is a restricted flow from the pump throughthe cup and into the discharge port I28. Insuch event, it is desirable to have the valve I34 loaded likewise, so that the flow through it to the outlet I28 is identical. This is accomplished by the fluid in the outlet I28 backingup into the chamber I44 and passing down along. the valve stem of the valve I48 into the chamber I62. Fluid likewise. in the event provision is so made, maypass down the sides between the valve I40 and the cylinder walls, in the area-indicated at I50. This fluid, reflecting the pressure in the outlet I28, is conducted into the annulus I32 by means of the port I58.

Referring next to Fig. 5, the fluid is conducted from the annulus I32 by the channel I30, and discharged into the annulus or throttling valve chamber I34'where it exerts anupward pressure against the bottom 01 the companion valve I40, by fllling the chamber I62 in said valve chamber I34 at the pressure of the fluid in the chamber I62 of the valve I86. This pressure moves the head of the valve I40 to a position identical with that of the. same valve in the other chamber, 'so

that substantially the same amount of fluid passes preferably the clearance being between .0005 and the head of the valve I48 in both units from the outlet I20. The excess fluid in the two chambers I82'will pass back into the respective outlets I28 and I28 when the unequal drag has been released. This backflow ordinarily will take place by seepage around the stem of the valve I48,.although other means of evacuating it may be provided if desired.

In the event it is desired to reverse the flow of fluid in the system, manipulation of the control 28 will result in fluid in the lines 52 and 54 returning through the ports I28 and I28 respectively, will enter the small ports I48 and chamber I44, will lift the disc valve I48 from its seat on the head of the valve I40, and will pass around the said disc valve I48 into the ports I I8 and'I20,

and flow back through the gear divider (now running in a reverse direction) into the chamber I I0 and back to the control means 28. This reversal of flow will occur ordinarily where the wing flaps are returned to the normal position after having been forced into a different position by means of the flow of the divider pumps above mentioned.

Referring next to Figures 4 and 5, it is noted that the device may be provided with means for relieving excessive pressure developed by expansion of the fluid in the system, such expansion as that which may be caused by heat, for example. 1 This comprises a small port I12, located in the housing of the device, which port connects at one end to the channel I30, and at the other end to. the relief chamber I14. The chamber I14 is, in turn, preferably closed by a hollow p108 II8 through which there is a small opening, and

to which plug there is attached a conduit capable oi carrying the very minute flow ordinarily passing through this device. This conduit'may be directed back to the supply tank. Check means, such as spring pressed ball check valve I18, normally closes the discharge and of the port I12 so that only under urging of the pressure caused by fluid expansion will the valve I18 I The channels 240 and 242 are likewise interconnected by means of what may be termed a "bypass" 244.

be provided with a thermal relief 248 which may be similar too'r identical with the relief arrangement described in connection with numerals I12,

be unseated and the fluid passed to the conduit leading to the supply tank.

Referring next to the construction shown schematically in Fig. 6 and in detail in Figs. 7, 8, 9', 10

and 11', there is illustrated the four-way fluid moving flow divider such as 56 Or 58. As will be clear from Fig. 6, many features of this device are I interconnected by fluid conducting means so that the flow from each stream is metered in the correct proportion for operating the wing flaps The modifications, however, comprises,

or other instrumentalities driven by the device.

Further, a,.modifled form of throttling valve is disclosed in which use is made of ballcheck means and in which the synthetic seal comparable to the seal I84 shown in Fig. 3 is eliminated. This is important especially since synthetic materials are scarce and expensive at this time, and difliculty is experienced in obtaining them for the purposes herein'disclosed. Further, the

synthetic seals may deteriorate under certain gen eral conditions whereas the ball 'checkvalves will not be likely so to do. Other advantages are clearly apparent.

More specifically, and still referring to Fig. 6 in particular and the schematic arrangement therein shown, the supply of fluid is brought to l the device by means of the pipe 52 or the like. A portion of this fluid enters the 'flrst inlet I80,

. and a second portion is divided oil through the inlet I82. The inlet I80 conducts the fluid into the top two set's of gears as illustrated in Fig. 6,

I74, I I6 and I I8 above set forth, in describing the device of Figs. 2, 3, 4 and 5.

It isunderstood thatthe arrangement ofFig. 6 is contemplated as for a single housing com-prising a compact structure and has many obvious advantages in such an embodiment. The housing is illustrated generally, for schematic purposes, as housing I8'I.

shown in Figs. '7, 8, 9, 10, and 11, and first to Fig. '7, thehousin I8! is shown as having a center plate 2I2, provided with gear-receiving recesses M4 and ZIB into which several sets of gears are inserted. These gears comprise, in the illustration of Fig. 7, for example, the gear wheels I 92 and I94 (on the shaft204 which is journaled in said center plate), one of said gear wheels being on each side of said center plate 2I2; a second set of gears I98 and I98 on a splined shaft 206, said gears I96 and I98 .being drivingly connected to said shaft 206 (gear I96 being on one side of said center plate 2I2 and gear I 98 being on the other side of said center plate 2I2), said shaft passing through said center plate 2I2 and being journaled for rotation therethrough; a third set of gears 200 and 202 journaled in a manner similar to the gears I92 and I94, the gears 200 and 202 being carried by the shaft 208. The side or cover plates H8 and 220 seat over the center plate and gears, and are provided with recesses for the ends of the shafts 204,206 and 208. The shaft 206 is preferably journaled in the bearings 2I0 so as to be freely rotatable with a minimum of friction. The side plates 2I8 and 220 form the side bushings for the outsides of the gear wheels, and thecenter plate 2I2 forms the bushingbe'tween the gear wheels and operates as a, divider separating flow of thefluid entering the gear wheels. I

As will be more clearly apparent from Fig. 9, the shafts 204 and 208 may be fixed to the center plate so that they do not rotate, or may be adapted to rotate, as desired. In any event, it is preferable to provide the bearings 248, for each shaft, on which the gear wheels I92, I94, 200

where it is divided and one-half of it is divided between the dischargeports I84 and I88, and the other half is divided between the discharge ports I88 and I90. The fluid entering the second inlet I82 is conducted to the gears shown as the center gear and the bottom gear (on the reverse I side as compared with the inlet I80) and the cenbly 236, and the discharge port I90 directs-its fluid through the throttle valve assembly 238.

The throttle valves 234 and 232 are interconnected by means of the fluid channels 242, and the throttle valves 236 and 238. are interconnected by means of the fluid moving channel 240.

and 202 may freely rotate.

Referring next to Fig. 8', there is illustrated the details of the construction embodied in valves 232, 234, 236 and. 238. Inasmuch as the construction is substantially identical inall of these four valves, the valve 232 will be described In detail with occasional reference to the valve 236 it being understood that the description generally, unless otherwise stated, relates to all four ball type equalizer or throttling valves.

This equalizer or throttling valve comprises an v inlet chamber 250 into which the discharge part I84 discharges fluid pumped by the gear wheels I92 and I96. This inlet chamber 250 is preferably formed of a cylindrical bore in the side plate (220 in this instance), the bore being of reduced diameter at the area adjacent the end of the discharge port I84 forming an annular ledge 25I. Preferably, a bushing 252 seats on a ledge portion 25I', formed by reduction of the diameter of the chamber. This annular bushing 252 preferably'is provided with a seal 254 which prevents the passage of fluid between the bushing and the cylinder wall.

The by-pass 244 may, if desired,-

Referring more to the actual embodiment pointed out.

stricted bore of the normally prevents the flow of fluid from the The bushing 252 forms a valve seat as hereinafter described, and llkewise'forms a shoulder or seat for a bushing 253 which is preferably cylindrical in shape, and extends lengthwise the bore in the housing side plate 226 to a position preferably slightly spaced axially of the bore from the inner limit of movement of the cap 266. This bushing 253 is likewise preferably reduced reduced in outside diameter as will be apparent by the drawings, the reduced diameter being.

' which in turn communicate with the annulus 264,

formed between thewalls of the bore of the valve chamber and a reduced portion of the side wall 'of the bushing 253. This annulus 264 connects to the outlet 224 (see Fig. 6).

The bushing 253 likewise has a seal 266, which prevents substantial flow of fluid between the walls of the bore and the bushing 253. This bushing 253 may if desired, be an integral part of bushing 252, or may be welded or otherwise attached to bushing 252, but for convenience in v In operation fluid from the discharge port l64,' which usually connects to the pump, enters the chamber 256' under pressure. It will exert force on the valve 266 and unseat the valve from the annular ledge portion of the bushing 252. The

fluid will flow around the valve head no and into the opening 262 from where it is conducted to the conduit leading to the fluid motor or de* vice to be operated. In this respect, the device works in synchronism with the other valves in the system. In the event the device to be operated in one of the other valves, for example invalve 234, becomes overloaded, fluid pressure from the channel 24: caused by the flow of fluid manufacture and assembly is preferably separate.

' It has a close fit with the side walls of the iongitudinal bore in the housing, and is normally stationary therein, removable only for repair and replacement. The bushing 253 is preferably tubular, and receives the longitudinally movable valve assembly 266. This valve assembly 266' has the enlarged valve head 216, which seats on the ledge portlon of the member 252. The valve 266 has a hollow bore 269, and this hollow space communicates with the openings 262, so that fluid may enter the ports 212 from sald openings 262.

The enlarged head-216 of ,thevalve 266 has an enlarged bore portion forming a seat for a valve, preferably ball valve 214 is ordinarily spring pressed by the spring 216.,into a'sealing valve 216. The spring 216 in turn is held in position by means era-longitudinally extending rod like member 216. This member 218 likewise prevents the ball 214- from becoming displaced and moving out of the enlarged bore of the valve head 216. The ball 214 effectively closes the bore 269 of the valve 266 against the flow of fluid from the discharge port I64 into said bore 269 without displacement of the valve 266.

At its opposite end, the bore of the valv'e 266 preferably is reduced in diameter between the ball 214 and the ports 212, and with a smaller ball valve 266 which is contained in still another chamber portion 282 formed in the valve 266 by enlarging the bore 269 thereof near its end as shown in Fig. 8. This ball 266 is spring pressed against the seat formed by the rechamber portion 269 and a ball type valve 214.- This relation with the valve seat 211 formed iii the enlarged bore of the to the chamber port i84'and be conducted into the system.

in said valve 234 down past the check ball 266, will be conducted into the valve 232 and will cause th fluid under pressure to move up against the check ball 266 of the valve 232. This, in turn, will force the valve 266 into a more seated position of the bushing 252, tending to close the opening past the head 216 so that fluid in the chamber 256 will not flow past the head 216 or, if it does flow, will be in metered amounts.

It will thus be seen that the pressure existing in the ports 262 will be equalized for all of the valves in the system. An excess of pressure in the chamber 269 will thus displace. the ball 266, and will balance the other valves withrelation to the valve 232 in the manner above described.

In the event of reversal of flow in the device,

be displaced and the fluid will flow from the ports 262 into the chamber 269 past the ball 214, into i the chamber 256, where it will enter the discharge .Referring next to the construction indicated in Fig. 12,-there is provided a modification in which the driving means is indicated as a motor such as an electric motor. In this construction,

thepump housing comprises a dividing wall 286, with side plates 296 and 292. Two sets of gears 294 and 296 form one gear pump, and a second set of gears 296 and 366 form a second gear pump. The gears 294 and 296- are shown as splined on a shaft 362 which forms the drive shaft for the" gear pump, and which is journaled for rotation in the housing. Appropriate bushings 364 and 366 are provided in connection with the side plates 296 and 292 respectively, and roller bearings 366 and 316, assure easy rotation of the shaft 362. The shaft-362passes through the dividing wall 266, and is extended on through a cover plate 31.4 on the side wall 292 in a conventional manner, the sealing ring 3i6 cooperating with an enlarged centering. portion 3i6 on the shaft 362 to prevent the leakage of fluid from the housing. The shaft 362 is provided with a toothed or splined gear-like member 326 which engages a complementary socket-like portion of the drlVe shaft 322 of the power motor 324. This forms the driving connection for gear pumps 294. 296 and 268 and 366. The gears 296 and 366 are joumaled on a shaft 326 on which they rotate. The'outlets 326 and 336 carry fluid from the fluid pump of the gears 296, 366 and the gears 294. 296 respectively. Equalizer valves, such as the valves illustrated in Figs. 2 and 3 or in Fig.6. are shown at 332 and 334.

By use of the motor driven arrangement, it is apparent that fluid from a low pressure means may be divided and equalized and used to drive a plurality of fluid motors in Fig. 1.

It is understoo indicated schematically that the foregoing description is' merely illustrative of a preferred embodiment of the invention and that the scope of the invention, therefore, is not to be limited thereto' but is to be determined by the appended claims.

Iclaim:

1. In a deviceoi' the class described, the com- I bination of a housing, a fluid inlet connection for said housing, divider means dividing said housing into two separate compartments, fluid moving gear means in each compartment, fluid connections between each 'said gear means and sad inlet, equalizer valve means for each gear means, fluid connections from said equalizer valve means to said gear means, and a fluid connection from the equalizer valve of one gear means to ,the equalizer valve of the other gear means, and separate discharge outlet means for each gear means, the entire construction being located withthe equalizer valve 01' one pump means to'the equalizer valve of the other pump means, separate discharge outlet means for each pump means, the entire construction being located within said housing means and being compact, and a power means drivingly connected to operate each pump means in synchronism with the other pump means. v

3. A compact divider means comprising a housing, a fluid inlet in said housing, a plurality of compartments in said housing, fluid moving gear means comprising a pump in each compartment, fluid conduit means between said inlet and the gear means of each compartment, a-separate fluid outlet from the gear means of eachcompartment, a separate throttling valve in connection with each outlet, fluid connection means between all throttling valves in said housing, all of said throttling valves, in response to variations of output pressure in any one or all of said pump outlets, restricting the output flow of each gear pump to an amount proportionate to the other gear pumps. I I

4. A compact divider means comprising a housing, a fluid inlet in said housing, a plurality oi compartments in said housing, fluid moving gear means comprising a pump in each compartment, fluid conduit means between said inlet and the pump means on each side of said divider opin said housing, a three-gear pump means located on each side'of said divider means, fluid connections from said inlet to two positions on each pump means, two discharge outlets for each pump means whereby means operatively connected to the pump means on each side of said divider operate in synchronism, an equalizer valve for each discharge of each pump means, connections between the equalizer valve of one outlet and theequalizer valves of the other pump outlets in said housing, whereby said pumps pump a substantially proportional amount of fluid into each discharge outlet regardless of pressure in said outlet.

.6. In adevice oi the class described the combination of a housing, a single inlet means in said .housing for fluid under pressure, a divider means in said housing, a three-gear pump means located on each side of said divider means, fluid connections from said inlet to two positions on each pump means, two discharge outlets for each pump means whereby means operatively connected to erate in synchronism, an equalizer valve for each discharge of tween the equalizer valve of one outlet and the equalizer valves of the other pump outlets in said housing, whereby said pumps pump a substantially proportional amount of fluid into each discharge outlet regardless of pressure in said outlet, and power means comprising an electric motor driving said gear means.

7. In a compact fluid moving flow divider, a housing, inlet means introducing fluid to said housing, a divider means separating said housing into a plurality of pump chambers, a plurality of sets of gears, one gear 01' each set being ineach chamber, said gears forming a plurality of pump .means, fluid conduit means connecting said inlet to each or said pump compartments, each pump fluid outlet from the gear means of each compartment, a separate throttling valve in connection with each outlet, fluid connectio'nmeans between all throttling valves in said said throttling valves, in response to variations oi output pressure in any one'or all oi said pump outlets, restricting the output flow oi each gear pump to an amount proportionate to theother gear pumps, each of said fluid moving gear means being operatively driven. in synchronism by a power means such as an electric motor,

5. In a device oi. the class described the combination of a housing, a single inlet means in said housing for fluid under pressure, a divider means housing, all of nism, discharge outlet means compartment having a plurality charge outlets, there being one outlet than sets or gears means regulating from each outlet.

8. In a compact inlet connection and a gear means, those of combining ina separating the housing into. two separate compartments, a fluid moving gear set in each compartment and connections from each compartment to said inlet, an equalizer valve'i'or each compartment, fluid connections between said equalizer valves, motor means directly connected to at least one of said gears, and a plurality of discharge outlets ments, there being; at leastone more discharge outlet than sets of gears in said housing.

9. In a compact inlet and a plurality oi compartments, those improvements which consist of combining in a sinof separate dismore discharge in said housing, and the amount of flow discharged plurality of fluid moving improvements which consist gle housing a plurality of gear trains, one located in each compartment, a single driving means to: both gear trains, which driving means. comprises motor connections to one gear of each gear train wherebysaid gear trains are driven in synchroproviding two discharge connections for each gear train, and equalizing valve means'equaling the pressure in both discharge outlets.

com; A. moon.

each pump means, connections begear divider havin a fluid.

single housing, divider means leading from said compart-' gear divider having a fluid 

